200911619 九、發明說明 【發明所屬之技術領域】 本發明相關於根據申請專利範圍請求項第1項的前言 部份的自行車的輪轂傳動裝置。此類型的輪轂傳動裝置可 從例如 D E 1 0 2 0 0 4 0 1 1 0 5 2 A 1 得知。 【先前技術】 內部安裝的多速輪轂傳動裝置被安裝於自行車的後車 輪，且容許自行車的騎車者選擇不同的齒輪比（gear ratio) 以改變踩踏力。典型上，輪轂傳動裝置包含安裝於自行車 車架的輪轂軸。輪轂軸可旋轉地支撐驅動件，以用來將踩 踏力經由鏈輪及鏈條而傳遞至輪轂傳動裝置。輪轂傳動裝 置另外包含同樣地由輪轂軸可旋轉地支撐的輪轂殼。 輪轂殼收納動力傳輸機構，而此動力傳輸機構被設置 在驅動件與輪轂殼之間，以用來將旋轉動力從驅動件傳遞 至輪轂殼。動力傳輸機構提供可藉由換檔機構來選擇的具 有不同齒輪比的多個動力傳輸路徑，其中每一個動力傳輸 路徑典型上產生特定的齒輪比。爲建立此多個動力傳輸路 徑，動力傳輸機構一般包含數個行星齒輪機構。 目前的內部輪轂傳動裝置被設計來提供十個或十個以 上的速率級。根據DE 1 0 2004 0 1 1 052 A1的輪轂傳動裝 置容許在由多個行星齒輪機構提供的九個速率級之間做選 擇。此已知的輪轂傳動裝置包含三個行星齒輪機構，其容 許將三個速率級與另外五個速率級組合，以有在3 40%的 200911619 齒輪比之下的總共九個速率級。此輪轂傳動裝置包含第一 行星齒輪機構，其包含不可旋轉地安裝於輪轂軸的第一中 心齒輪、由第一行星齒輪托架可旋轉地支撐的第一行星齒 輪、及第一環形齒輪。第一行星齒輪被設置在第一中心齒 輪與第一環形齒輪之間，且與第一中心齒輪及第一環形齒 輪嚙合。 第二行星齒輪機構包含被配置在第一行星齒輪托架上 的第二中心齒輪。第二行星齒輪被安裝在第一環形齒輪上 〇 第三行星齒輪機構類似於第二行星齒輪機構而形成， 且包含安裝在第一行星齒輪托架上的第三中心齒輪。第三 中心齒輪與第三行星齒輪嚙合，而第三行星齒輪的每一個 不可旋轉地結合於各別的第二行星齒輪。藉此，形成二階 (two-step)行星齒輪。第三行星齒輪與第二環形齒輪嚙合 ，以將第三行星齒輪機構的轉矩傳遞至第二行星齒輪機構 〇 此輪轂傳動裝置的換檔機構包含棘爪托架（pawl carrier)，其容許將驅動件選擇性地與各別行星齒輪機構 的組件耦接，以產生不同的齒輪比。爲此目的，棘爪托架 包含藉由三個換檔凸輪來致動的多個可控制的棘爪（亦即 六個棘爪）。 二階行星齒輪在第一環形齒輪上的配置結合上與二階 行星齒輪嚙合的第二環形齒輪導致堆疊式的內部輪轂傳動 裝置。因爲第二環形齒輪與三個行星齒輪機構的其他組件 -5- 200911619 重疊，所以第二環形齒輪的直徑且因此內部輪轂傳動裝置 的直徑增大。另外，內部輪轂傳動裝置的堆疊式構造導致 輪轂的總重量增大。 如前所述，第二及第三中心齒輪的每一個都被安裝在 第一行星齒輪托架上。因此，第二及第三中心齒輪的每一 個都與第一行星齒輪托架一起繞輪轂軸旋轉。特別是，速 率級8及9的動力傳輸路徑包含驅動件、第六棘爪、及第一 ί了星齒輪托架，其中第一行星齒輪繞第一中心齒輪旋轉。 動力傳輸路徑另外包含第一環形齒輪、第二環形齒輪、第 一棘爪、將動力傳輸機構與輪轂殼連接的棘爪、及輪轂殼 。於速率級8，第二行星齒輪繞第二中心齒輪旋轉，且於 速率級9，第二行星齒輪繞第二中心齒輪旋轉。 由於行星齒輪機構的此有差別的旋轉型式，動力傳輸 路徑很複雜，特別是速率級8及9的動力傳輸路徑，因此其 傳遞動力的效率極低。 類似的輪轂傳動裝置可從DE 1 97 2 0 796 Α1得知，其 揭示具有串聯配置的多個行星齒輪機構的多速輪轂。所揭 示的輪轂傳動裝置可達成7速換檔或1 4速換檔。1 4速輪轂 傳動裝置包含五個行星齒輪機構，其組件可被選擇性地鎖 定以建立所想要的動力傳輸路徑。第一行星齒輪機構包含 由輪轂軸可旋轉地支撐的第一中心齒輪，其可與輪轂軸鎖 定在一起。第一中心齒輪與由第一行星齒輪托架可旋轉地 支撐的二階行星齒輪的較小直徑嚙合。第一行星齒輪托架 與輪轂殼不可旋轉地連接。 -6- 200911619 二階行星齒輪的大直徑與環形齒輪嚙合，而環形齒輪 可與輪轂軸或與第一中心齒輪鎖定在一起。 第二行星齒輪機構包含由輪轂軸可旋轉地支撐且可與 輪轂軸鎖定在一起的第二中心齒輪。第二行星齒輪與第二 中心齒輪及第二環形齒輪嚙合，其中第二環形齒輪與第一 中心齒輪不可旋轉地連接。 第三行星齒輪機構包含由輪轂軸可旋轉地支撐且可與 輪轂軸鎖定在一起的第二中心齒輪。第二彳了星齒輪與第三 中心齒輪嚙合，而第三中心齒輪與各別第二行星齒輪不可 旋轉地連接。第二中心齒輪與階梯狀（s t e p p e d )行星齒輪的 小直徑階段嚙合，且第三中心齒輪與階梯狀行星齒輪的大 直徑階段嚙合。 第四及第五行星齒輪機構類似於第二及第三行星齒輪 機構，且對稱地形成及被配置。因此，第四及第五行星齒 輪機構同樣地包含二階行星齒輪，其中第二及第三行星齒 輪機構的行星齒輪及第四及第五行星齒輪機構的行星齒輪 藉著共同的行星齒輪托架而被可旋轉地支撐。第四及第五 行星齒輪機構的階梯狀行星齒輪的小直徑階段與和驅動件 不可旋轉地連接的環形齒輪嚙合。 1 4速輪轂傳動裝置的另外實施例是根據上述輪轂傳動 裝置的修改實施例，且包含與對稱地配置的階梯狀行星齒 輪的二小直徑階段均嚙合的第二環形齒輪。共同的行星齒 輪托架由兩個分開的行星齒輪托架取代，其中第二及第三 行星齒輪機構的行星齒輪托架與第一中心齒輪不可旋轉地 200911619 連接。第四及第五行星齒輪機構的行星齒輪托架與驅動件 不可旋轉地連接。 由於鎖定行星齒輪機構的分開的組件（例如環形齒輪 與中心齒輪）所需的離合器的數目增加’因此根據DE 1 97 20 796 A1的輪轂傳動裝置很複雜且相較之下很昂貴。 【發明內容】 本發明的目的爲提供一種自行車的輪轂傳動装置，其 包含多個速率級且可達成重量輕及小型的構造。 根據本發明，此目的是藉著包含申請專利範圍請求項 第1項所載的特徵的自行車的輪轂傳動裝置而達成。 本發明根據其技術思想提供一種自行車的輪轂傳動裝 置，其包含輪轂軸、驅動件、及輪轂殼，而驅動件及輪轂 殼的每一個都是由輪轂軸可旋轉地支撐。輪轂傳動裝置另 外包含動力傳輸機構，其被設置在驅動件與輪轂殼之間， 用來將旋轉動力從驅動件經由多個動力傳輸路徑而傳遞至 輪轂殼；及換檔機構，用來選擇上述的多個動力傳輸路徑 中的一個。動力傳輸機構包含多個行星齒輪機構，其中下 游行星齒輪機構的行星齒輪托架與上游行星齒輪機構的行 星齒輪嚙合。下游行星齒輪機構包含多於一個的中心齒輪 〇 根據本發明而形成的輪轂傳動裝置具有多項有利點。 因爲下游行星齒輪機構的行星齒輪托架與上游行星齒輪機 構的行星齒輪嚙合，所以達成小型的設計，其容許在保持 -8 - 200911619 輪轂的小直徑之下實現多個動力傳輸路徑。下游行星齒輪 托架與上游行星齒輪的上述耦接進一步容許藉著相較之下 簡單的結構來實現多個動力傳輸路徑，此降低傳動裝置的 組件故障的危險。 由於本發明的輪轂傳動裝置的令人驚異的簡單結構， 因此可用相當低的成本生產可達成相較之下更多數的齒輪 比的輪轂傳動裝置。因爲下游行星齒輪機構包含多於一個 的中心齒輪，所以根據本發明的輪轂傳動裝置容許實施1 5 個速率級。 在較佳實施例中，動力傳輸機構包含串聯配置的至少 五個行星齒輪機構。藉此，可用小型設計及相當小的輪轂 直徑來實現1 5速輪轂傳動裝置。 較佳地，下游行星齒輪機構包含第一及第二行星齒輪 機構，且上游行星齒輪機構包含至少第三、第四、及第五 行星齒輪機構。 第一及第二行星齒輪機構可包含下游行星齒輪機構的 行星齒輪托架。第四行星齒輪機構可包含上游行星齒輪機 構的行星齒輪。此表示第一及第二行星齒輪機構藉著與上 游行星齒輪嚙合的下游行星齒輪機構的行星齒輪托架而與 第四行星齒輪機構耦接。 較佳地，下游行星齒輪機構的行星齒輪托架包含托架 部份、及與上游行星齒輪機構的行星齒輪嚙合的環形齒輪 部份，其中托架部份與環形齒輪部份不可旋轉地連接，特 別是成整體地形成。因此，要強調的是下游行星齒輪機構 -9- 200911619 的行星齒輪托架履行兩項功能，亦即對於第一及第二行星 齒輪機構的行星齒輪的支撐功能，以及對於上游行星齒輪 機構的行星齒輪的動力傳輸功能。由於托架部份與環形齒 輪部份之間的不可旋轉的連接，因此輪轂傳動裝置的小型 設計被最佳化。 較佳地，下游行星齒輪機構的行星齒輪托架可與第五 行星齒輪機構連接。藉此，可實現數個另外的動力傳輸路 徑。 下游行星齒輪機構的行星齒輪托架與第五行星齒輪機 構的連接可例如藉著一較佳實施例而實現，其中下游行星 齒輪機構的行星齒輪托架包含離合器接合部份，而此離合 器接合部份可與第五行星齒輪機構的行星齒輪托架連接。 爲使旋轉力從下游行星齒輪機構的行星齒輪托架傳輸 至輪轂殼，下游行星齒輪機構的行星齒輪托架較佳地可藉 著第一離合器而與輪轂殼連接。 在較佳實施例中，第一行星齒輪機構另外包含由輪轂 軸可旋轉地支撐且可與輪轂軸鎖定在一起的第一中心齒輪 、與第一中心齒輪同軸地配置的第一環形齒輪、及與第一 中心齒輪及第一環形齒輪嚙合的多個第一行星齒輪，其中 第一行星齒輪由第一行星齒輪機構的行星齒輪托架可旋轉 地支撐。第一行星齒輪機構爲下游行星齒輪機構的部份。 第二行星齒輪機構可包含由輪轂軸可旋轉地支撐且可 與輪轂軸鎖定在一起的第二中心齒輪、與第二中心齒輪同 軸地配置的第一環形齒輪、及與第二中心齒輪及第一環形 -10- 200911619 齒輪嚙合的多個第二行星齒輪，其中第二行星齒輪由第一 行星齒輪機構的行星齒輪托架可旋轉地支撐，且第一及第 二行星齒輪分別不可旋轉地連接，特別是成整體地形成， 以形成階梯狀行星齒輪。第二行星齒輪機構也爲下游行星 齒輪機構的部份。 如此，下游行星齒輪機構包含多於一個的中心齒輪， 亦即第一及第二中心齒輪。下游行星齒輪機構的第一及第 二中心齒輪（一般而言，多於一個的中心齒輪）與第一及第 二行星齒輪機構的行星齒輪嚙合，且與下游行星齒輪機構 的（共同）行星齒輪托架相互作用。 較佳地，第一環形齒輪可藉著第二離合器而與輪轂殼 連接，以用來將旋轉力從第一環形齒輪傳遞至輪轂殼。 第三行星齒輪機構可包含由輪轂軸可旋轉地支撐且可 與輪轂軸鎖定在一起的第三中心齒輪、相對於輪轂軸被可 旋轉地支撐的第二行星齒輪托架、及由第二行星齒輪托架 可旋轉地支撐且與第三中心齒輪嚙合的多個第三行星齒輪 〇 第四行星齒輪機構可包含由輪轂軸可旋轉地支撐且可 與輪轂軸鎖定在一起的第四中心齒輪，其中上游行星齒輪 機構而特別是第四行星齒輪機構的行星齒輪由第二行星齒 輪托架可旋轉地支撐且與第四中心齒輪嚙合。 第四行星齒輪機構的行星齒輪與第三行星齒輪機構的 第三行星齒輪分別不可旋轉地連接，特別是成整體地形成 ，以形成階梯狀行星齒輪。 -11 - 200911619 在另外的較佳實施例中，第五行星齒輪機構包含不可 旋轉地固定於輪轂軸的第五中心齒輪、與第五中心齒輪同 軸地配置的第二環形齒輪、及由第三行星齒輪托架可旋轉 地支撑的多個第五行星齒輪，其中第五行星齒輪與第五中 心齒輪及第二環形齒輪嚙合。 第三行星齒輪托架可與第二行星齒輪托架接合。 第三離合器可被設置在第三行星齒輪托架與第一行星 齒輪托架特別是離合器接合部份之間，以用來將旋轉力從 第三行星齒輪托架傳遞至第一行星齒輪托架。第四離合器 可被設置在驅動件與第二環形齒輪之間，以用來將旋轉力 從驅動件傳遞至第二環形齒輪。第五離合器可被設置在驅 動件與第三行星齒輪托架之間，以用來將旋轉力從驅動件 傳遞至第三行星齒輪托架。 以下會藉著例子且參考圖式來敘述本發明。 【實施方式】 圖1顯示可被安裝於自行車的後車輪的根據本發明的 輪轂傳動裝置的實施例。此輪轂傳動裝置包含輪轂軸1、 及由輪轂軸1可旋轉地支撐的驅動件2。輪轂傳動裝置另外 包含由輪轂軸1可旋轉地支撐的輪轂殼3。動力傳輸機構4 被設置在驅動件2與輪轂殼3之間，用來將旋轉動力從驅動 件2經由可依騎車者所想要的被選擇以改變齒輪比的多個 動力傳輸路徑而傳遞至輪轂殼3。換檔機構5被設置來選擇 上述多個動力傳輸路徑中的一個。 -12- 200911619 換檔機構5相應於此處所提及的E P 1 3 2 3 6 2 7 A 2及美 國專利第6,6 0 7,4 6 5 B 1號中詳細敘述的換檔機構。 動力傳輸機構4包含包括下游行星齒輪機構及上游行 星齒輪機構的多個行星齒輪機構6、7、8、9、10’其中上 游行星齒輪機構被配置成爲比下游行星齒輪機構較爲靠近 驅動件2。如在旋轉動力流程的方向中所見的，下游行星 齒輪機構被配置在上游行星齒輪機構之後。例如，下游行 星齒輪機構包含第一及第二行星齒輪機構6、7，而上游行 星齒輪機構包含第三、第四、及第五行星齒輪機構8、9、 1 〇。第一及第二行星齒輪機構6、7 (下游行星齒輪機構）可 與第四行星齒輪機構9(上游行星齒輪機構）耦接。 上述多個行星齒輪機構6、7、8、9、1 0被串聯配置， 且包含至少五個行星齒輪機構6、7、8、9、10。行星齒輪 機構6、7、8、9、1 〇的編號越高，則其被配置成越靠近驅 動件2。例如’第二行星齒輪機構7比第一行星齒輪機構6 靠近驅動件2。 如從圖1很明顯的，下游行星齒輪機構包含行星齒輪 托架31，並且上游行星齒輪機構包含行星齒輪44’其中下 游或第一及第二行星齒輪機構6、7的行星齒輪托架31與上 游或第四行星齒輪機構9的行星齒輪44嚙合。行星齒輪托 架31爲第一及第二行星齒輪機構7二者用的共同托架。 一般而言’行星齒輪托架3丨具有縱向延伸的形狀，其 可與配置在第一及第二行星齒輪機構6、7的上游的動力傳 輸機構4的組件重疊，且因此與下游行星齒輪機構6、7相 -13- 200911619 比較爲靠近驅動件2。 特別是，下游行星齒輪機構6、7的行星齒輪托架3 1從 下游或第一及第二行星齒輪機構6、7的區域軸向延伸至上 游或第四行星齒輪機構9的區域。如圖1所示，行星齒輪托 架3 1軸向延伸超過輪轂傳動裝置的整個長度的1 /3以上至 1 /2。行星齒輪托架3 1的軸向延伸係成爲使得配置在下游 行星齒輪機構6、7與上游而特別是第四行星齒輪機構9之 間的第三行星齒輪機構8被行星齒輪托架3 1重疊。在根據 圖1的實施例中，第三行星齒輪機構8不與行星齒輪托架3 1 接合。 行星齒輪托架3 1包含階梯狀形狀，其中後續階梯的內 部直徑朝向驅動件2增大。行星齒輪托架3 1的階梯狀形狀 會在以下連同與其相關聯的各別組件被更詳細地敘述。 行星齒輪托架3 1另外包含（第一）離合器接合部份3 1 c ，其被配置在靠近驅動件2的行星齒輪托架3 1的軸向端部 上。離合器接合部份31c被設置來接合/脫離離合器53 (第 三離合器），此會在以下相關於第五行星齒輪機構1 〇被更 詳細地敘述。 行星齒輪托架3 1另外包含環形齒輪部份3 1 b。環形齒 輪部份3 1 b與離合器接合部份3 1 c成整體地連接，且形成 爲具有比離合器接合部份3 1 c小的內部直徑。環形齒輪部 份3 1 b與上游或第四行星齒輪機構9的行星齒輪44嚙合。 環形齒輪部份3 1 b的內部直徑比第三行星齒輪機構8的第 三行星齒輪43的外部直徑大，以避免與其接合或碰撞。 -14- 200911619 環形齒輪部份3 1 b與托架部份3 1 a成整體地連接’而 托架部份3 1 a支撐第一下游行星齒輪機構6的第一行星齒 輪4 1及第二下游行星齒輪機構7的第二行星齒輪42。第一 行星齒輪4 1由第一行星齒輪軸4 1 a可旋轉地支撐。第二行 星齒輪42由第二行星齒輪軸42a可旋轉地支撐。第一及第 二行星齒輪軸41a、42a被設置在行星齒輪托架31的托架 部份31a中。典型上，三個或三個以上的第一行星齒輪41 及第二彳了星齒輪4 2被分別设置在弟一及弟一 fr星齒輪機構 6、7 中。 另一個（或第二）離合器接合部份3 1 d與托架部份3 1 a 成整體地形成，且被設置用來接合/脫離第一離合器51 ’ 以建立/中斷從行星齒輪托架31至輪轂殼3的動力傳輸。另 一個（或第二）離合器接合部份31d被配置在第一行星齒輪 機構6的下游。環形齒輪部份3 1 b及（弟一' )離合器接合部份 3 1 c位在行星齒輪機構6的上游。再次地’組件的下游或 上游配置是在動力流程的方向中所見及應從動力流程的方 向來瞭解的。 以下敘述上述的多個行星齒輪機構6、7、8、9、1 0。 第一行星齒輪機構6被配置在最下游或最遠離驅動件2 ，且包含由輪轂軸1可旋轉地支撐且可與輪轂軸1鎖定在一 起的第一中心齒輪1 1。在第一中心齒輪1 1的內周邊表面與 輪轂軸1之間，第一中心齒輪導環6 1被不可旋轉地固定於 輪轂軸1。第一中心齒輪導環6 1容許藉著換檔機構5而鎖定 及釋放第一中心齒輪1 1。 -15- 200911619 上述的多個第一行星齒輪41由第一行星齒輪托架31而 特別是由設置在第一行星齒輪托架31中的第—行星齒輪軸 4 1 a可旋轉地支撐’且與第—中心齒輪丨丨嚙合。 第二行星齒輪機構7被配置在第一行星齒輪機構6的上 游’且包含由輪轂軸1可旋轉地支撐且可與輪轂軸1鎖定在 —起的第二中心齒輪12。第二中心齒輪導環62容許藉著換 檔機構5而鎖定及釋放第二中心齒輪〗2。 如圖1中所見的，第一中心齒輪i〗及第二中心齒輪1 2( 一般而言’多於一個或至少兩個的中心齒輪）相鄰於彼此 被配置。 第一及第二中心齒輪11、12( —般而言，多於一個或 至少兩個的中心齒輪）可與輪轂軸1鎖定在一起。 第一中心齒輪1 1及第二中心齒輪1 2形成下游行星齒輪 機構的部份，其藉著第一行星齒輪托架3 1而與上游行星齒 輪機構或第四行星齒輪機構9的行星齒輪4 4耦接。 如在圖1中另外所見的，第二中心齒輪12包含於下游 軸向方向延伸的軸向凸出部12a。軸向凸出部l2a在徑向 上被配置在與第一行星齒輪4 1嚙合的第一中心齒輪1 1的接 合部份的下方。爲此目的，中心齒輪1 1包含順應第二中心 齒輪1 2的軸向凸出部1 2 a的肩部。藉此，達成第一及第二 中心齒輪1 1、1 2的小型且穩定的組態。 第二行星齒輪機構7另外包含與第二中心齒輪1 2嚙合 的第二行星齒輪42。相關於輪轂軸1同軸地配置且由輪轂 軸1可旋轉地支撐的爲第一環形齒輪2 1，其與第二行星齒 -16- 200911619 輪機構7的第二行星齒輪4 2嚙合，使得第二行星齒輪4 2被 配置在第一環形齒輪2 1與第二中心齒輪1 2之間。第二行星 齒輪42由第二行星齒輪軸42a支撐。第二行星齒輪軸42a 被設置在第一行星齒輪托架3 1中。 第二行星齒輪軸42a與第一行星齒輪軸41a成整體地 形成，使得第一及第二行星齒輪4 1、42由相同或共同的軸 41a、42a 支撑。 如圖1所示，第一及第二行星齒輪41、42形成兩個齒 輪階段（g e a r s t a g e )，其中第一行星齒輪4 1的大直徑齒輪階 段與第一中心齒輪1 1嚙合，且第二行星齒輪4 2的小直徑齒 輪階段與第一環形齒輪2 1嚙合。第二行星齒輪42的小直徑 齒輪階段被配置成爲靠近第三行星齒輪機構8。第一及第 二行星齒輪4 1、42不可旋轉地耦接，特別是成整體地形成 〇 藉此，第一及第二行星齒輪41、42構成包含二不同直 徑的階梯狀或不可旋轉地耦接的行星齒輪，其與第一及第 二中心齒輪1 1、1 2 ( —般而言，與至少兩個中心齒輪1 1、 1 2)嚙合。階梯狀行星齒輪的大直徑與第一中心齒輪11嚙 合，而階梯狀行星齒輪的小直徑與第二中心齒輪1 2及第一 環形齒輪2 1嚙合。 此至少兩個中心齒輪1 1、1 2可藉著第一行星齒輪托架 3 1而與上游行星齒輪機構而特別是第四行星齒輪機構9耦 接。 第一環形齒輪2 1可藉著設置在第一環形齒輪2 1與輪轂 -17- 200911619 殼3之間的第二（單向）離合器52而與輪轂殼3連接或分離。 如上所述，第一行星齒輪機構6的行星齒輪托架3 1於 輪轂傳動裝置的縱向方向軸向延伸超過第一及第二行星齒 輪4 1、4 2，因而與至少接續地配置的上游第三及第四行星 齒輪機構8、9重疊。第一行星齒輪托架3 1的外部輪廓可部 份地順應第一環形齒輪2 1且形成肩部3 1 e，使得第一環形 齒輪21被配置在肩部31e與第一行星齒輪41的大直徑齒輪 階段之間。 第三行星齒輪機構8位在第二行星齒輪機構7的上游， 且包含由輪轂軸1可旋轉地支撐且可與輪轂軸1鎖定在一起 的第三中心齒輪1 3。在第三中心齒輪1 3的內表面與輪轂軸 1之間，第三中心齒輪導環63被不可旋轉地固定於輪轂軸1 。多個第三行星齒輪43由被輪轂軸1可旋轉地支撐的第二 行星齒輪托架32可旋轉地支撐。爲此目的，第三行星齒輪 43由被第二行星齒輪托架32支撐的第三行星齒輪軸43a可 旋轉地支撐。典型上，設置有三個或三個以上的第三行星 齒輪4 3。 第四行星齒輪機構9被配置在第三行星齒輪機構8的上 游，且包含由輪轂軸1可旋轉地支撐且可與輪轂軸1鎖定在 —起的第四中心齒輪14。在第四中心齒輪Μ的內周邊表面 與輪轂軸1之間，第四中心齒輪導環64被配置且不可旋轉 地固定於輪轂軸1。第四中心齒輪導環64可藉著換檔機構5 而被致動來鎖定/釋放第四中心齒輪1 4。 多個第四彳了星齒輪44與弟四中心囫輪14 D菌合’且由弟 -18- 200911619 二行星齒輪托架3 2可旋轉地支撐。特別是，第四行星齒輪 44被配置在第四行星齒輪軸44a上，而第四行星齒輪軸 44a與第三行星齒輪軸43a成整體地形成，且因此代表第 三及第四行星齒輪4 3、4 4的共同行星齒輪軸。 如從圖1很明顯的，第三及第四行星齒輪43、44不可 旋轉地連接且成整體地形成階梯狀行星齒輪402。階梯狀 行星齒輪402的小直徑齒輪階段（第三行星齒輪43)與第三 中心齒輪1 3嚙合，且階梯狀行星齒輪402的大直徑齒輪階 段（第四行星齒輪44)與第四中心齒輪14嚙合。另外，階梯 狀行星齒輪402的大直徑齒輪階段（第四行星齒輪44)與下 游的行星齒輪托架3 1的環形齒輪部份3 1 b嚙合。如此，可 建立將第四中心齒輪1 4與第一行星齒輪托架3 1連接的傳輸 路徑。 第五行星齒輪機構1 〇被配置在第四行星齒輪機構9的 上游，且代表最靠近驅動件2的行星齒輪機構。第五行星 齒輪機構1 〇包含不可旋轉地固定於輪轂軸1的第五中心齒 輪1 5。第二環形齒輪2 2與輪轂軸1同軸地配置且由輪轂軸1 可旋轉地支撐。在第二環形齒輪22與第五中心齒輪1 5之間 ，多個第五行星齒輪45被配置成爲形成爲二階行星齒輪。 第五行星齒輪45的大直徑齒輪階段與第二環形齒輪22嚙合 ，且第五行星齒輪4 5的小直徑齒輪階段與第五中心齒輪1 5 嚙合。典型上，設置有三個或三個以上的第五行星齒輪45 〇 第五行星齒輪4 5由可繞輪轂軸1旋轉的第三行星齒輪 -19- 200911619 托架33可旋轉地支撐。第三行星齒輪托架33包含可旋轉地 支撑第五行星齒輪45的第五行星齒輪軸45a。第三行星齒 輪托架33與第二行星齒輪托架32接合，以將動力從第三行 星齒輪托架33傳遞至第二行星齒輪托架32。 如從圖1非常明顯的，第三及第四行星齒輪軸43 a、 4 4 a的中心軸線與第五行星齒輪軸4 5 a的中心軸線在徑向 上間隔開。第五行星齒輪軸4 5 a的中心軸線被配置在一圓 柱形平面上’而此圓柱形平面具有比含有第三及第四行星 齒輪軸4 3 a、4 4 a的中心軸線的圓柱形平面大的直徑。含 有第一及第二行星齒輪軸4 1 a、4 2 a的中心軸線的圓柱形 平面相應於第五行星齒輪軸4 5 a的中心軸線的圓柱形平面 。如此’被配置在第二行星齒輪機構7與第五行星齒輪機 構1 〇之間的第三及第四行星齒輪軸4 3 a、4 4 a的中心軸線 分別比第二及第五行星齒輪軸4 2 a、4 5 a的中心軸線較爲 靠近輪轂軸1。 第五行星齒輪機構1 0的第三行星齒輪托架3 3可連接於 下游的行星齒輪托架3 1。爲此目的，以上提及的第三離合 器53被設置在第三行星齒輪托架33與第一行星齒輪托架31 之間。特別是，第三離合器5 3被配置在遠離驅動件2的第 三行星齒輪托架3 3的端部處，且接合/脫離下游的第一行 星齒輪托架3 1的離合器接合部份3 1 c。對於從驅動件2至第 五行星齒輪機構10的動力傳輸，設置有第四離合器54及第 五離合器55。 第四離合器54爲設置在驅動件2與第二環形齒輪22之 -20- 200911619 間的單向離合器。第二環形齒輪22包含朝向驅動件2延伸 的軸向凸出部22a。軸向凸出部22a在其內周邊表面上包 含離合器接合部份22b，其與第四離合器54合作以將第二 環形齒輪22與驅動件2鎖定在一起或互相釋放。第四離合 器5 4由平行於環形齒輪2 2的軸向凸出部2 2 a延伸的驅動件 2的軸向凸出部2a支撐。 對於速率級1至8，第四離合器54與環形齒輪22接合， 以將動力從驅動件2傳遞至環形齒輪2 2。 對於速率級9至15，在驅動件2與第三行星齒輪托架33 之間設置有第五離合器5 5，以用來將旋轉動力從驅動件2 傳遞至第三行星齒輪托架33。第五離合器55形成爲離合器 環，且可於輪轂軸1的縱向方向軸向移動。第五離合器55 包含兩個接合部份55a、55b，其可分別與設置在驅動件2 及第三行星齒輪托架33上的離合器接合部份2b及33a接合 〇 驅動件2的離合器接合部份2b形成在軸向凸出部2a的 內周邊表面上，且與第五離合器55的上方或徑向接合部份 5 5b接合。第三行星齒輪托架33的離合器接合部份33a可 接合/脫離第五離合器5 5的下方或軸向接合部份5 5 a。 對於速率級9至1 5，第五離合器5 5的軸向接合部份5 5 a 與第三行星齒輪托架3 3的離合器接合部份3 3 a耦接，而第 四離合器54分離。 前述的離合器機構包括第四及第五離合器54及55的更 詳細敘述揭示在均爲本案申請人所擁有的EP 1 3 2 3 6 2 7 -21 - 200911619 A2以及歐洲專利申請案07 00 1 076.4中。 根據圖1的輪轂傳動裝置的作用及功能可參考圖2至j 6 來說明，其中各圖顯示對於每一個速率級的不同組件的輔 接以及藉此實現的特定動力傳輸路徑。圖2至1 6中所示的 粗線及箭頭顯示通過動力傳輸機構4的旋轉動力流程。不 同組件的耦接以及動力傳輸路徑顯示在以下的表1及2中， 其中表1是關於組件的耦接’而表2是關於特定的動力傳輸 路徑。 表1 速率級 離合器環55 (驅動件與第三行 星齒輪托架33) 第一中心 齒輪11 第二中心 齒輪12 第三中心 齒輪13 第四中心 齒輪14 1 脫離 自由 自由 自由 自由 2 脫離 鎖定 自由 自由 自由 3 脫離 自由 自由 自由 鎖定 4 脫離 自由 _自由 鎖定 自由 5 脫離 鎖定 自由 自由 鎖定 6 脫離 鎖定 自由 鎖定 自由 7 脫離 自由 鎖定 自由 鎖定 8 脫離 自由 鎖定 鎖定 自由 9 接合 鎖定 自由 自由 自由 10 接合 自由 自由 自由 鎖定 11 接合 自由 自由 鎖定 自由 12 _ 接合 鎖定 自由 自由 鎖定 13 接合 鎖定 自由 鎖定 自由 14 接合 自由 鎖定 自由 鎖定 15 接合 自由 鎖定 鎖定 自由 -22- 200911619 表2 速率級 動力傳輸路徑 齒輪比 1 驅動件-第四離合器54-第二環形齒輪22-(第五行星齒輪 45繞第五中心齒輪15旋轉)-第三行星齒輪托架33-第三離 合器53 -第一行星齒輪托架31 -第一離合器51 -輪轂殼 0.426 2 驅動件-第四離合器54-第二環形齒輪22-(第五行星齒輪 45繞第五中心齒輪15旋轉)-第三行星齒輪托架33-第三離 合器53-第一行星齒輪托架31-(第一行星齒輪41繞第一中 心齒輪11旋轉)-第一環形齒輪21-第二離合器52-輪轂殼 0.545 3 驅動件-第四離合器54-第二環形齒輪22-(第五行星齒輪 45繞第五中心齒輪15旋轉)-第三行星齒輪托架33-第二行 星齒輪托架32-(第四行星齒輪44繞第四中心齒輪14旋轉 )-第一行星齒輪托架31 -第一離合器51 ·輪轂殼 0.612 4 驅動件-第四離合器54-第二環形齒輪22-(第五行星齒輪 45繞第五中心齒輪15旋轉)-第三行星齒輪托架33-第二行 星齒輪托架32-(第三行星齒輪43繞第三中心齒輪13旋轉 )-第一行星齒輪托架31 -第一離合器51 -輪轂殼 0.694 5 驅動件-第四離合器54-第二環形齒輪22-(第五行星齒輪 45繞第五中心齒輪15旋轉)-第三行星齒輪托架33-第二行 星齒輪托架32-(第四行星齒輪44繞第四中心齒輪14旋轉 )-第一行星齒輪托架31-(第一行星齒輪41繞第一中心齒 輪11旋轉)-第一環形齒輪21-第二離合器52-輪轂殼 0.782 6 驅動件-第四離合器54-第二環形齒輪22-(第五行星齒輪 45繞第五中心齒輪15旋轉)-第三行星齒輪托架33-第二行 星齒輪托架32-(第三行星齒輪43繞第三中心齒輪13旋轉 )-第一行星齒輪托架31-(第一行星齒輪41繞第一中心齒 輪11旋轉)-第一環形齒輪21-第二離合器52-輪轂殼 0.887 7 驅動件-第四離合器54-第二環形齒輪22-(第五行星齒輪 45繞第五中心齒輪15旋轉)-第三行星齒輪托架33-第二行 星齒輪托架32-(第四行星齒輪44繞第四中心齒輪14旋轉 )-第一行星齒輪托架31-(第二行星齒輪42繞第二中心齒 輪12旋轉)-第一環形齒輪21 -第二離合器52-輪轂殼 0.997 -23- 200911619 8 驅動件-第四離合器54-第二環形齒輪22-(第五行星齒輪 45繞第五中心齒輪15旋轉)-第三行星齒輪托架33-第二行 星齒輪托架32-(第三行星齒輪43繞第三中心齒輪13旋轉 )-第一行星齒輪托架31-(第二行星齒輪42繞第二中心齒 輪12旋轉)-第一環形齒輪21-第二離合器52-輪轂殼 1.130 9 驅動件-第五離合器55-第三行星齒輪托架33-第三離合器 53-第一行星齒輪托架31-(第一行星齒輪41繞第一中心齒 輪11旋轉)-第一環形齒輪21-第二離合器52-輪轂殼 1.279 10 驅動件-第五離合器55-第三行星齒輪托架33-第二行星齒 輪托架32-(第四行星齒輪44繞第四中心齒輪14旋轉)-第 一行星齒輪托架31 -第一離合器51 -輪轂殼 1.437 11 驅動件-第五離合器55-第三行星齒輪托架33-第二行星齒 輪托架32-(第三行星齒輪43繞第三中心齒輪13旋轉)-第 一行星齒輪托架31 -第一離合器51 -輪轂殼 1.630 12 驅動件-第五離合器55-第三行星齒輪托架33-第二行星齒 輪托架32-(第四行星齒輪44繞第四中心齒輪14旋轉)-第 一ί了星齒輪托架31-(第一行星齒輪41繞第一中心齒輪11 旋轉)_第一環形齒輪21-第二離合器52-輪轂殼 1.838 13 驅動件-第五離合器55-第三行星齒輪托架33-第二行星齒 輪托架32-(第三行星齒輪43繞第三中心齒輪13旋轉)-第 一行星齒輪托架31-(第一行星齒輪41繞第一中心齒輪11 旋轉)-第一環形齒輪21-第二離合器52-輪轂殼 2.085 14 驅動件·第五離合器55-第三行星齒輪托架33-第二行星齒 輪托架32-(第四行星齒輪44繞第四中心齒輪14旋轉)-第 一行星齒輪托架31-(第二行星齒輪42繞第二中心齒輪12 旋轉)-第一環形齒輪21-第二離合器52-輪轂殼 2.341 15 驅動件-第五離合器55-第三行星齒輪托架33-第二行星齒 輪托架32-(第三行星齒輪43繞第三中心齒輪13旋轉)-第 一行星齒輪托架31-(第二行星齒輪42繞第二中心齒輪12 旋轉)-第一環形齒輪21-第二離合器52-輪轂殼 2.656 -24- 200911619 綜上所述，根據所敘述的本發明的實施例的輪轂傳動 裝置容許實現15速內部輪轂傳動裝置，其中輪轂殼2的直 徑類似於目前可得的8速輪轂傳動裝置的直徑。此表示本 發明的輪轂傳動裝置在不增加輪轂直徑之下提供比傳統輪 轂傳動裝置多的速率級。另外，根據圖1的輪轂傳動裝置 提供所有的傳輸路徑均簡單的有利點，此導致有效率的動 力傳輸。 —般而言，下游的行星齒輪機構6的行星齒輪托架3 1 具有可與上游的行星齒輪機構8的行星齒輪43嚙合的軸向 伸長形狀。另外’行星齒輪托架3 1的軸向伸長形狀容許行 星齒輪托架3 1與更上游的行星齒輪機構9的行星齒輪托架 3 3耦接/分離。特別是，下游的行星齒輪機構6的軸向伸長 的行星齒輪托架3 1可選擇性地從上游的行星齒輪機構8的 行星齒輪4 3傳輸旋轉動力，且可選擇性地從更上游的行星 齒輪機構9的行星齒輪托架3 3傳輸旋轉動力。 下游的行星齒輪托架3 i的軸向伸長形狀容許有具有極 高效率的傳輸路徑的自行車用的小型 '小直徑的內部輪轂 傳動裝置。 【圖式簡單說明】 圖1爲根據本發明的實施例的輪轂傳動裝置的縱向剖 面圖。 圖2爲根據圖丨的輪轂傳動裝置於速率級〗的縱向剖面 圖。 -25- 200911619 圖3爲根據圖1的輪轂傳動裝置於速率級2的縱向剖面 圖。 圖4爲根據圖1的輪轂傳動裝置於速率級3的縱向剖面 圖。 圖5爲根據圖1的輪轂傳動裝置於速率級4的縱向剖面 圖。 圖6爲根據圖1的輪轂傳動裝置於速率級5的縱向剖面 圖。 圖7爲根據圖1的輪轂傳動裝置於速率級6的縱向剖面 圖。 圖8爲根據圖1的輪轂傳動裝置於速率級7的縱向剖面 圖。 圖9爲根據圖1的輪轂傳動裝置於速率級8的縱向剖面 圖。 圖1 〇爲根據圖1的輪轂傳動裝置於速率級9的縱向剖面 圖。 圖1 1爲根據圖1的輪轂傳動裝置於速率級i 〇的縱向剖 面圖。 圖1 2爲根據圖1的輪轂傳動裝置於速率級〗丨的縱向剖 面圖。 圖1 3爲根據圖1的輪轂傳動裝置於速率級丨2的縱向剖 面圖。 圖1 4爲根據圖1的輪轂傳動裝置於速率級丨3的縱向剖 面圖。 -26- 200911619 圖1 5爲根據圖1的輪轂傳動裝置於速率級1 4的縱向剖 面圖。 圖1 6爲根據圖1的輪轂傳動裝置於速率級1 5的縱向剖 面圖。 【主要元件符號說明】 1 :輪穀軸 2 :驅動件 2 a :軸向凸出部 2 b :離合器接合部份 3 : 輪轂殼 4 :動力傳輸機構 5 :換檔機構 6 :第一行星齒輪機構 7 :第二行星齒輪機構 8 :第三行星齒輪機構 9 :第四行星齒輪機構 1 0 :第五行星齒輪機構 1 1 :第一中心齒輪 1 2 :第二中心齒輪 1 2 a :軸向凸出部 1 3 :第二中心齒輪 1 4 :第四中心齒輪 1 5 :第五中心齒輪 -27 - 200911619 2 1 :第一環形齒輪 22 :第二環形齒輪 22a :軸向凸出部 22b :離合器接合部份 3 1 :第一行星齒輪托架 3 1 a :托架部份 3 1 b :環形齒輪部份 3 1 c :離合器接合部份 3 1 d :離合器接合部份 3 1 e :肩部 3 2 :第二行星齒輪托架 3 3 :第三行星齒輪托架 3 3 a :離合器接合部份 41 :第一行星齒輪 4 1 a :第一行星齒輪軸 42 :第二行星齒輪 4 2 a :第二行星齒輪軸 4 3 :第三行星齒輪 4 3 a :第三行星齒輪軸 44 :第四行星齒輪 4 4 a :第四行星齒輪軸 4 5 :第五行星齒輪 4 5 a :第五行星齒輪軸 5 1 :第一離合器 -28 - 200911619 52 :第二離合器 53 :第三離合器 54 :第四離合器 55:第五離合器，離合器環 5 5 a :下方或軸向接合部份 5 5 b :上方或徑向接合部份 6 1 :第一中心齒輪導環 62 :第二中心齒輪導環 63 :第三中心齒輪導環 64 :第四中心齒輪導環 402 :階梯狀行星齒輪 -29-BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bicycle hub transmission device according to the preamble of claim 1 of the claims. This type of hub transmission is known, for example, from D E 1 0 2 0 0 4 0 1 1 0 5 2 A 1 . [Prior Art] The internally mounted multi-speed hub transmission is mounted to the rear wheel of the bicycle, and allows the bicycle rider to select different gear ratios to change the pedaling force. Typically, the hub transmission includes a hub axle mounted to the bicycle frame. The hub axle rotatably supports the drive member for transmitting the pedaling force to the hub transmission via the sprocket and the chain. The hub transmission device additionally includes a hub shell that is likewise rotatably supported by the hub axle. The hub shell houses a power transmission mechanism that is disposed between the drive member and the hub shell for transmitting rotational power from the drive member to the hub shell. The power transmission mechanism provides a plurality of power transmission paths having different gear ratios selectable by a shifting mechanism, wherein each of the power transmission paths typically produces a particular gear ratio. To establish the plurality of power transmission paths, the power transmission mechanism generally includes a plurality of planetary gear mechanisms. Current internal hub transmissions are designed to provide ten or more speed levels. The hub transmission according to DE 1 0 2004 0 1 1 052 A1 allows selection between nine speed stages provided by a plurality of planetary gear mechanisms. This known hub transmission includes three planetary gear mechanisms that allow three speed stages to be combined with five other speed stages to have a total of nine speed levels below the 3,410% 200911619 gear ratio. The hub transmission includes a first planetary gear mechanism including a first central gear non-rotatably mounted to the hub axle, a first planetary gear rotatably supported by the first planetary gear carrier, and a first ring gear. The first planetary gear is disposed between the first center gear and the first ring gear and meshes with the first sun gear and the first ring gear. The second planetary gear mechanism includes a second sun gear that is disposed on the first planet gear carrier. The second planetary gear is mounted on the first ring gear. The third planetary gear mechanism is formed similar to the second planetary gear mechanism and includes a third sun gear mounted on the first planetary gear carrier. The third sun gear meshes with the third planet gear, and each of the third planet gears is non-rotatably coupled to the respective second planet gear. Thereby, a two-step planetary gear is formed. The third planetary gear meshes with the second ring gear to transmit the torque of the third planetary gear mechanism to the second planetary gear mechanism. The shifting mechanism of the hub transmission includes a pawl carrier that allows The drive members are selectively coupled to the components of the respective planetary gear mechanisms to produce different gear ratios. For this purpose, the pawl bracket contains a plurality of controllable pawls (i.e., six pawls) actuated by three shifting cams. The arrangement of the second-order planetary gears on the first ring gear in combination with the second ring gear meshing with the second-order planetary gears results in a stacked internal hub transmission. Since the second ring gear overlaps with the other components of the three planetary gear mechanisms -5 - 200911619, the diameter of the second ring gear and thus the diameter of the inner hub transmission increases. In addition, the stacked configuration of the internal hub transmission results in an increase in the overall weight of the hub. As previously mentioned, each of the second and third sun gears is mounted on the first planet gear carrier. Therefore, each of the second and third sun gears rotates around the hub axle together with the first planet gear carrier. In particular, the power transmission paths of the speed stages 8 and 9 include a drive member, a sixth pawl, and a first planetary gear carrier, wherein the first planetary gear rotates about the first sun gear. The power transmission path additionally includes a first ring gear, a second ring gear, a first pawl, a pawl that connects the power transmission mechanism to the hub shell, and a hub shell. At rate level 8, the second planet gear rotates about the second sun gear, and at rate stage 9, the second planet gear rotates about the second sun gear. Due to this differential rotation pattern of the planetary gear mechanism, the power transmission path is complicated, especially the power transmission paths of the speed stages 8 and 9, so that the efficiency of transmitting power is extremely low. A similar hub transmission is known from DE 1 97 2 0 796 , 1, which discloses a multi-speed hub having a plurality of planetary gear mechanisms arranged in series. The disclosed hub transmission can achieve a 7-speed shift or a 14-speed shift. 1 4 Speed Hub The transmission consists of five planetary gear mechanisms whose components can be selectively locked to establish the desired power transmission path. The first planetary gear mechanism includes a first sun gear rotatably supported by the hub axle that is lockable with the hub axle. The first sun gear meshes with a smaller diameter of the second-order planet gear rotatably supported by the first planet gear carrier. The first planet gear carrier is non-rotatably coupled to the hub shell. -6- 200911619 The large diameter of the second-order planetary gear meshes with the ring gear, and the ring gear can be locked with the hub axle or with the first sun gear. The second planetary gear mechanism includes a second sun gear that is rotatably supported by the hub axle and that is lockable with the hub axle. The second planetary gear meshes with the second sun gear and the second ring gear, wherein the second ring gear is non-rotatably coupled to the first sun gear. The third planetary gear mechanism includes a second sun gear that is rotatably supported by the hub axle and that is lockable with the hub axle. The second planetary gear meshes with the third sun gear, and the third sun gear is non-rotatably coupled to the respective second planetary gear. The second sun gear meshes with the small diameter stage of the stepped (s t e p p e d ) planet gear, and the third sun gear meshes with the large diameter stage of the stepped planet gear. The fourth and fifth planetary gear mechanisms are similar to the second and third planetary gear mechanisms and are symmetrically formed and configured. Therefore, the fourth and fifth planetary gear mechanisms similarly include a second-order planetary gear, wherein the planetary gears of the second and third planetary gear mechanisms and the planetary gears of the fourth and fifth planetary gear mechanisms are coupled by a common planetary gear carrier It is rotatably supported. The small diameter stages of the stepped planetary gears of the fourth and fifth planetary gear mechanisms mesh with a ring gear that is non-rotatably coupled to the drive member. A further embodiment of a 4 speed hub transmission is in accordance with a modified embodiment of the hub transmission described above and includes a second ring gear that meshes with both small diameter stages of the symmetrically arranged stepped planet gears. The common planetary gear carrier is replaced by two separate planetary gear carriers, wherein the planetary gear carriers of the second and third planetary gear mechanisms are non-rotatably connected to the first sun gear 200911619. The planet gear carriers of the fourth and fifth planetary gear mechanisms are non-rotatably coupled to the drive member. The number of clutches required to lock the separate components of the planetary gear mechanism, such as the ring gear and the sun gear, is increased. The hub transmission according to DE 1 97 20 796 A1 is therefore complicated and relatively expensive. SUMMARY OF THE INVENTION It is an object of the present invention to provide a bicycle hub transmission that includes a plurality of speed stages and that achieves a lightweight and compact construction. According to the invention, this object is achieved by a hub transmission of a bicycle comprising the features of claim 1 of the claim. The present invention provides a bicycle hub transmission device according to its technical idea, which comprises a hub axle, a drive member, and a hub shell, and each of the drive member and the hub shell is rotatably supported by the hub axle. The hub transmission additionally includes a power transmission mechanism disposed between the driving member and the hub shell for transmitting rotational power from the driving member to the hub shell via the plurality of power transmission paths; and a shifting mechanism for selecting the above One of a plurality of power transmission paths. The power transmission mechanism includes a plurality of planetary gear mechanisms, wherein the planetary gear carrier of the downstream planetary gear mechanism meshes with the planetary gear of the upstream planetary gear mechanism. The downstream planetary gear mechanism comprises more than one sun gear. The hub gear formed in accordance with the present invention has a number of advantages. Since the planet carrier of the downstream planetary gear mechanism meshes with the planet gears of the upstream planetary gear mechanism, a compact design is achieved which allows multiple power transmission paths to be achieved while maintaining the small diameter of the hub -8 - 200911619. The aforementioned coupling of the downstream planetary gear carrier with the upstream planetary gear further allows for multiple power transmission paths by a relatively simple construction, which reduces the risk of component failure of the transmission. Thanks to the surprisingly simple construction of the hub transmission of the present invention, a hub transmission that achieves a greater number of gear ratios can be produced at a relatively low cost. Since the downstream planetary gear mechanism contains more than one sun gear, the hub transmission according to the present invention allows for the implementation of 15 speed stages. In a preferred embodiment, the power transmission mechanism includes at least five planetary gear mechanisms arranged in series. In this way, a 15 speed hub transmission can be realized with a small design and a relatively small hub diameter. Preferably, the downstream planetary gear mechanism includes first and second planetary gear mechanisms, and the upstream planetary gear mechanism includes at least third, fourth, and fifth planetary gear mechanisms. The first and second planetary gear mechanisms may include planet gear carriers of the downstream planetary gear mechanism. The fourth planetary gear mechanism may include planetary gears of the upstream planetary gear mechanism. This means that the first and second planetary gear mechanisms are coupled to the fourth planetary gear mechanism by the planetary gear carrier of the downstream planetary gear mechanism that meshes with the upstream planetary gear. Preferably, the planetary gear carrier of the downstream planetary gear mechanism includes a bracket portion and a ring gear portion that meshes with the planetary gear of the upstream planetary gear mechanism, wherein the bracket portion is non-rotatably coupled to the ring gear portion. In particular, it is formed integrally. Therefore, it is emphasized that the planetary gear carrier of the downstream planetary gear mechanism -9-200911619 performs two functions, namely, the supporting function of the planetary gears of the first and second planetary gear mechanisms, and the planet for the upstream planetary gear mechanism. The power transmission function of the gear. The small design of the hub transmission is optimized due to the non-rotatable connection between the bracket portion and the ring gear portion. Preferably, the planet gear carrier of the downstream planetary gear mechanism is connectable to the fifth planetary gear mechanism. Thereby, several additional power transmission paths can be realized. The connection of the planetary carrier of the downstream planetary gear mechanism to the fifth planetary gear mechanism can be achieved, for example, by a preferred embodiment, wherein the planetary gear carrier of the downstream planetary gear mechanism includes a clutch engagement portion and the clutch engagement portion The part can be coupled to the planet gear carrier of the fifth planetary gear mechanism. To transmit rotational force from the planet gear carrier of the downstream planetary gear mechanism to the hub shell, the planet gear carrier of the downstream planetary gear mechanism is preferably coupled to the hub shell by the first clutch. In a preferred embodiment, the first planetary gear mechanism additionally includes a first sun gear rotatably supported by the hub axle and lockable with the hub axle, a first ring gear coaxially disposed with the first sun gear, And a plurality of first planet gears meshing with the first sun gear and the first ring gear, wherein the first planet gears are rotatably supported by the planet gear carrier of the first planetary gear mechanism. The first planetary gear mechanism is part of the downstream planetary gear mechanism. The second planetary gear mechanism may include a second sun gear rotatably supported by the hub axle and lockable with the hub axle, a first ring gear coaxially disposed with the second sun gear, and a second sun gear and First ring-10-200911619 a plurality of second planetary gears meshed by the gear, wherein the second planetary gear is rotatably supported by the planetary gear carrier of the first planetary gear mechanism, and the first and second planetary gears are respectively non-rotatable The ground connection, in particular, is integrally formed to form a stepped planetary gear. The second planetary gear mechanism is also part of the downstream planetary gear mechanism. As such, the downstream planetary gear mechanism includes more than one sun gear, namely the first and second sun gears. The first and second sun gears of the downstream planetary gear mechanism (generally, more than one sun gear) mesh with the planet gears of the first and second planetary gear mechanisms, and the (common) planetary gears of the downstream planetary gear mechanism Bracket interaction. Preferably, the first ring gear is coupled to the hub shell by a second clutch for transmitting rotational force from the first ring gear to the hub shell. The third planetary gear mechanism may include a third sun gear rotatably supported by the hub axle and lockable with the hub axle, a second planet gear carrier rotatably supported relative to the hub axle, and a second planet a plurality of third planetary gears rotatably supported by the gear carrier and meshing with the third sun gear, the fourth planetary gear mechanism may include a fourth sun gear rotatably supported by the hub axle and lockable with the hub axle, The planetary gear of the upstream planetary gear mechanism, and particularly the fourth planetary gear mechanism, is rotatably supported by the second planetary gear carrier and meshes with the fourth sun gear. The planetary gear of the fourth planetary gear mechanism and the third planetary gear of the third planetary gear mechanism are respectively non-rotatably connected, in particular integrally formed, to form a stepped planetary gear. -11 - 200911619 In a further preferred embodiment, the fifth planetary gear mechanism includes a fifth sun gear non-rotatably fixed to the hub axle, a second ring gear coaxially disposed with the fifth sun gear, and a third A plurality of fifth planetary gears rotatably supported by the planetary gear carrier, wherein the fifth planetary gear meshes with the fifth sun gear and the second ring gear. The third planet gear carrier is engageable with the second planet gear carrier. a third clutch may be disposed between the third planetary carrier and the first planetary carrier, particularly the clutch engagement portion, for transmitting rotational force from the third planetary carrier to the first planetary carrier . A fourth clutch may be disposed between the drive member and the second ring gear for transmitting rotational force from the drive member to the second ring gear. A fifth clutch is disposed between the drive member and the third planet gear carrier for transmitting rotational force from the drive member to the third planetary gear carrier. The invention will be described below by way of example and with reference to the drawings. [Embodiment] Fig. 1 shows an embodiment of a hub transmission according to the present invention which can be mounted to a rear wheel of a bicycle. This hub transmission comprises a hub axle 1 and a drive member 2 rotatably supported by the hub axle 1. The hub transmission additionally includes a hub shell 3 rotatably supported by the hub axle 1. The power transmission mechanism 4 is disposed between the driving member 2 and the hub shell 3 for transmitting rotational power from the driving member 2 via a plurality of power transmission paths that are selected by the rider to change the gear ratio. To the hub shell 3. The shifting mechanism 5 is arranged to select one of the plurality of power transmission paths. -12- 200911619 The shifting mechanism 5 corresponds to the shifting mechanism described in detail in E P 1 3 2 3 6 2 7 A 2 and U.S. Patent No. 6,6 0 7, 4 6 5 B 1 . The power transmission mechanism 4 includes a plurality of planetary gear mechanisms 6 , 7 , 8 , 9 , 10 ′ including a downstream planetary gear mechanism and an upstream planetary gear mechanism, wherein the upstream planetary gear mechanism is configured to be closer to the driving member 2 than the downstream planetary gear mechanism . As seen in the direction of the rotary power flow, the downstream planetary gear mechanism is disposed after the upstream planetary gear mechanism. For example, the lower procession gear mechanism includes first and second planetary gear mechanisms 6, 7 and the upper procession gear mechanism includes third, fourth, and fifth planetary gear mechanisms 8, 9, 1 . The first and second planetary gear mechanisms 6, 7 (downstream planetary gear mechanism) are coupled to the fourth planetary gear mechanism 9 (upstream planetary gear mechanism). The plurality of planetary gear mechanisms 6, 7, 8, 9, 10 are arranged in series and include at least five planetary gear mechanisms 6, 7, 8, 9, 10. The higher the number of the planetary gear mechanisms 6, 7, 8, 9, 1 〇 is, the closer it is to the drive member 2. For example, the second planetary gear mechanism 7 is closer to the driving member 2 than the first planetary gear mechanism 6. As is apparent from Fig. 1, the downstream planetary gear mechanism includes the planetary carrier 31, and the upstream planetary gear mechanism includes the planetary gear 44' with the planetary gear carrier 31 of the downstream or first and second planetary gear mechanisms 6, 7 and The planetary gears 44 of the upstream or fourth planetary gear mechanism 9 mesh. The planet gear carrier 31 is a common carrier for both the first and second planetary gear mechanisms 7. In general, the 'planetary carrier 3' has a longitudinally extending shape that overlaps with the components of the power transmission mechanism 4 disposed upstream of the first and second planetary gear mechanisms 6, 7, and thus with the downstream planetary gear mechanism 6, 7-phase-13- 200911619 is compared to the drive 2. In particular, the planet gear carrier 31 of the downstream planetary gear mechanisms 6, 7 extends axially from the downstream or the region of the first and second planetary gear mechanisms 6, 7 to the region of the upstream or fourth planetary gear mechanism 9. As shown in Fig. 1, the planetary carrier bracket 31 extends axially beyond 1/3 of the entire length of the hub transmission to 1 /2. The axial extension of the planet carrier 3 1 is such that the third planetary gear mechanism 8 disposed between the downstream planetary gear mechanisms 6, 7 and the upstream, and in particular the fourth planetary gear mechanism 9, is overlapped by the planetary carrier 3 1 . In the embodiment according to Fig. 1, the third planetary gear mechanism 8 is not engaged with the planetary carrier 3 1 . The planetary gear carrier 31 includes a stepped shape in which the inner diameter of the subsequent step is increased toward the driving member 2. The stepped shape of the planet gear carrier 3 1 will be described in more detail below in conjunction with the various components associated therewith. The planetary gear carrier 3 1 additionally includes a (first) clutch engagement portion 3 1 c which is disposed on an axial end portion of the planetary carrier 3 1 adjacent to the drive member 2. The clutch engagement portion 31c is provided to engage/disengage the clutch 53 (third clutch), which will be described in more detail below with respect to the fifth planetary gear mechanism 1 。. The planet gear carrier 3 1 additionally includes a ring gear portion 3 1 b. The ring gear portion 3 1 b is integrally coupled to the clutch engagement portion 3 1 c and is formed to have an inner diameter smaller than the clutch engagement portion 31 c. The ring gear portion 3 1 b meshes with the planetary gear 44 of the upstream or fourth planetary gear mechanism 9. The inner diameter of the ring gear portion 3 1 b is larger than the outer diameter of the third planetary gear 43 of the third planetary gear mechanism 8 to avoid engagement or collision therewith. -14- 200911619 The ring gear portion 3 1 b is integrally connected with the bracket portion 3 1 a ' and the bracket portion 3 1 a supports the first planetary gear 4 1 of the first downstream planetary gear mechanism 6 and The second planetary gear 42 of the downstream planetary gear mechanism 7. The first planetary gear 41 is rotatably supported by the first planetary gear shaft 4 1 a. The second planetary gear 42 is rotatably supported by the second planetary gear shaft 42a. The first and second planetary gear shafts 41a, 42a are disposed in the bracket portion 31a of the planetary carrier 31. Typically, three or more of the first planetary gears 41 and the second planetary gears 4 2 are respectively disposed in the brothers 1 and 1 of the fr star gear mechanisms 6, 7. The other (or second) clutch engagement portion 31d is integrally formed with the bracket portion 31a and is configured to engage/disengage the first clutch 51' to establish/disconnect from the planetary carrier 31. Power transmission to the hub shell 3. The other (or second) clutch engagement portion 31d is disposed downstream of the first planetary gear mechanism 6. The ring gear portion 3 1 b and the (part 1) clutch engagement portion 3 1 c are positioned upstream of the planetary gear mechanism 6. Again, the downstream or upstream configuration of the components is seen in the direction of the power flow and should be understood from the direction of the power flow. The plurality of planetary gear mechanisms 6, 7, 8, 9, 10 described above will be described below. The first planetary gear mechanism 6 is disposed at the most downstream or farthest from the drive member 2, and includes a first sun gear 11 that is rotatably supported by the hub axle 1 and that is lockable with the hub axle 1. Between the inner peripheral surface of the first sun gear 1 1 and the hub axle 1, the first sun gear guide ring 61 is non-rotatably fixed to the hub axle 1. The first sun gear guide ring 6 1 allows the first sun gear 11 to be locked and released by the shifting mechanism 5. -15- 200911619 The plurality of first planetary gears 41 described above are rotatably supported by the first planetary gear carrier 31 and particularly by the first planetary gear shaft 4 1 a provided in the first planetary carrier 31 Engages with the first - center gear 丨丨. The second planetary gear mechanism 7 is disposed upstream of the first planetary gear mechanism 6 and includes a second sun gear 12 rotatably supported by the hub axle 1 and lockable with the hub axle 1. The second sun gear guide ring 62 allows the second sun gear to be locked and released by the shifting mechanism 5. As seen in Fig. 1, the first sun gear i and the second sun gear 12 (generally more than one or at least two sun gears) are disposed adjacent to each other. The first and second sun gears 11, 12 (generally, more than one or at least two sun gears) can be locked with the hub axle 1. The first sun gear 1 1 and the second sun gear 12 form part of the downstream planetary gear mechanism, which is coupled to the planetary gear 4 of the upstream planetary gear mechanism or the fourth planetary gear mechanism 9 by the first planetary gear carrier 31 4 coupled. As seen additionally in Fig. 1, the second sun gear 12 includes an axial projection 12a extending in the downstream axial direction. The axial projection l2a is disposed radially below the engaging portion of the first sun gear 11 engaged with the first planetary gear 41. For this purpose, the sun gear 1 1 includes a shoulder that conforms to the axial projection 1 2 a of the second sun gear 1 2 . Thereby, a small and stable configuration of the first and second sun gears 1 1 and 1 2 is achieved. The second planetary gear mechanism 7 additionally includes a second planetary gear 42 that meshes with the second sun gear 12. Coordinated with respect to the hub axle 1 and rotatably supported by the hub axle 1 is a first ring gear 2 1 that meshes with a second planet gear 42 of the second planet gears 16-200911619 wheel mechanism 7 such that The second planetary gear 42 is disposed between the first ring gear 21 and the second sun gear 12. The second planetary gear 42 is supported by the second planetary gear shaft 42a. The second planetary gear shaft 42a is disposed in the first planetary gear carrier 31. The second planetary gear shaft 42a is integrally formed with the first planetary gear shaft 41a such that the first and second planetary gears 41, 42 are supported by the same or common shafts 41a, 42a. As shown in FIG. 1, the first and second planetary gears 41, 42 form two gear stages, wherein the large-diameter gear stage of the first planetary gear 41 meshes with the first sun gear 11 and the second planet The small diameter gear stage of the gear 42 meshes with the first ring gear 2 1 . The small diameter gear stage of the second planetary gear 42 is disposed close to the third planetary gear mechanism 8. The first and second planetary gears 4 1 , 42 are non-rotatably coupled, in particular integrally formed, whereby the first and second planetary gears 41 , 42 form a stepped or non-rotatably coupled coupling comprising two different diameters The coupled planet gears mesh with the first and second sun gears 1 1 , 1 2 (generally, with at least two sun gears 1 1 , 1 2 ). The large diameter of the stepped planetary gear meshes with the first sun gear 11, and the small diameter of the stepped planetary gear meshes with the second sun gear 12 and the first ring gear 21. The at least two sun gears 1 1 , 1 2 can be coupled to the upstream planetary gear mechanism, in particular the fourth planetary gear mechanism 9, by the first planetary carrier 3 1 . The first ring gear 21 can be coupled or disconnected from the hub shell 3 by a second (unidirectional) clutch 52 disposed between the first ring gear 21 and the hub -17-200911619. As described above, the planetary carrier 3 1 of the first planetary gear mechanism 6 extends axially beyond the first and second planetary gears 4 1 , 4 2 in the longitudinal direction of the hub transmission, and thus is arranged upstream with at least successively The third and fourth planetary gear mechanisms 8, 9 overlap. The outer contour of the first planetary gear carrier 31 may partially conform to the first ring gear 21 and form a shoulder 3 1 e such that the first ring gear 21 is disposed at the shoulder 31e and the first planetary gear 41 Large diameter gear between stages. The third planetary gear mechanism 8 is located upstream of the second planetary gear mechanism 7, and includes a third sun gear 13 that is rotatably supported by the hub axle 1 and that is lockable with the hub axle 1. Between the inner surface of the third sun gear 13 and the hub axle 1, the third sun gear guide ring 63 is non-rotatably fixed to the hub axle 1. The plurality of third planetary gears 43 are rotatably supported by a second planetary gear carrier 32 rotatably supported by the hub axle 1. For this purpose, the third planetary gear 43 is rotatably supported by the third planetary gear shaft 43a supported by the second planetary carrier 32. Typically, three or more third planetary gears 43 are provided. The fourth planetary gear mechanism 9 is disposed upstream of the third planetary gear mechanism 8, and includes a fourth sun gear 14 rotatably supported by the hub axle 1 and lockable with the hub axle 1. Between the inner peripheral surface of the fourth sun gear yoke and the hub axle 1, the fourth sun gear guide ring 64 is disposed and non-rotatably fixed to the hub axle 1. The fourth sun gear guide ring 64 can be actuated by the shifting mechanism 5 to lock/release the fourth sun gear 14 . A plurality of fourth planetary gears 44 and a four-centered wheel 14 are sterilized and are rotatably supported by a brother -18-200911619. In particular, the fourth planetary gear 44 is disposed on the fourth planetary gear shaft 44a, and the fourth planetary gear shaft 44a is integrally formed with the third planetary gear shaft 43a, and thus represents the third and fourth planetary gears 4 3 , 4 4 common planetary gear shaft. As is apparent from Fig. 1, the third and fourth planetary gears 43, 44 are non-rotatably coupled and integrally form a stepped planetary gear 402. The small-diameter gear stage (third planetary gear 43) of the stepped planetary gear 402 meshes with the third sun gear 13, and the large-diameter gear stage (fourth planetary gear 44) and the fourth sun gear 14 of the stepped planetary gear 402 Engage. Further, the large-diameter gear stage (fourth planetary gear 44) of the stepped planetary gear 402 meshes with the ring gear portion 3 1 b of the downstream planetary gear carrier 31. Thus, a transmission path connecting the fourth sun gear 14 to the first planetary gear carrier 31 can be established. The fifth planetary gear mechanism 1 〇 is disposed upstream of the fourth planetary gear mechanism 9 and represents the planetary gear mechanism closest to the drive member 2. The fifth planetary gear mechanism 1 〇 includes a fifth center gear 15 that is non-rotatably fixed to the hub axle 1. The second ring gear 22 is disposed coaxially with the hub axle 1 and rotatably supported by the hub axle 1. Between the second ring gear 22 and the fifth sun gear 15, the plurality of fifth planetary gears 45 are arranged to be formed as second-order planetary gears. The large-diameter gear stage of the fifth planetary gear 45 meshes with the second ring gear 22, and the small-diameter gear stage of the fifth planetary gear 45 meshes with the fifth sun gear 15. Typically, three or more fifth planetary gears 45 are provided. The fifth planetary gears 45 are rotatably supported by a third planetary gear -19-200911619 bracket 33 that is rotatable about the hub axle 1. The third planetary gear carrier 33 includes a fifth planetary gear shaft 45a that rotatably supports the fifth planetary gear 45. The third planetary gear carrier 33 is engaged with the second planetary carrier 32 to transfer power from the third planetary gear carrier 33 to the second planetary carrier 32. As is apparent from Fig. 1, the central axes of the third and fourth planetary gear shafts 43a, 4a are radially spaced from the central axis of the fifth planetary gear shaft 45a. The central axis of the fifth planetary gear shaft 45 5 a is disposed on a cylindrical plane having a cylindrical plane than the central axis containing the third and fourth planetary gear shafts 4 3 a, 4 4 a Large diameter. The cylindrical plane containing the central axes of the first and second planetary gear shafts 4 1 a, 4 2 a corresponds to a cylindrical plane of the central axis of the fifth planetary gear shaft 45 5 a. Thus, the central axes of the third and fourth planetary gear shafts 4 3 a, 4 4 a disposed between the second planetary gear mechanism 7 and the fifth planetary gear mechanism 1 分别 are respectively smaller than the second and fifth planetary gear shafts The central axis of 4 2 a, 4 5 a is closer to the hub axle 1 . The third planetary gear carrier 33 of the fifth planetary gear mechanism 10 is connectable to the downstream planetary gear carrier 31. For this purpose, the above-mentioned third clutch 53 is disposed between the third planetary carrier 33 and the first planetary carrier 31. In particular, the third clutch 53 is disposed at an end of the third planetary carrier 33 away from the drive member 2, and engages/disengages the clutch engagement portion 3 1 of the downstream first planetary carrier 3 1 c. For the power transmission from the driving member 2 to the fifth planetary gear mechanism 10, a fourth clutch 54 and a fifth clutch 55 are provided. The fourth clutch 54 is a one-way clutch disposed between the drive member 2 and the second ring gear 22 between -20 and 200911619. The second ring gear 22 includes an axial projection 22a that extends toward the drive member 2. The axial projection 22a includes a clutch engagement portion 22b on its inner peripheral surface that cooperates with the fourth clutch 54 to lock the second ring gear 22 with the drive member 2 or to release each other. The fourth clutch 5 4 is supported by an axial projection 2a of the driving member 2 which extends parallel to the axial projection 2 2 a of the ring gear 22. For rate stages 1 through 8, fourth clutch 54 is engaged with ring gear 22 to transfer power from drive member 2 to ring gear 22. For the speed stages 9 to 15, a fifth clutch 55 is provided between the drive member 2 and the third planetary carrier 33 for transmitting rotational power from the drive member 2 to the third planetary carrier 33. The fifth clutch 55 is formed as a clutch ring and is axially movable in the longitudinal direction of the hub axle 1. The fifth clutch 55 includes two engaging portions 55a, 55b that are engageable with the clutch engaging portions 2b and 33a provided on the driving member 2 and the third planetary carrier 33, respectively, to engage the clutch engaging portion of the driving member 2. 2b is formed on the inner peripheral surface of the axial projection 2a, and is engaged with the upper or radial engaging portion 55b of the fifth clutch 55. The clutch engagement portion 33a of the third planetary carrier 33 can engage/disengage the lower or axial engagement portion 55 5 a of the fifth clutch 55. For the speed stages 9 to 15, the axial engagement portion 5 5 a of the fifth clutch 5 5 is coupled to the clutch engagement portion 3 3 a of the third planetary carrier 33, and the fourth clutch 54 is disengaged. A more detailed description of the aforementioned clutch mechanism including the fourth and fifth clutches 54 and 55 is disclosed in EP 1 3 2 3 6 2 7 -21 - 200911619 A2 owned by the applicant and European Patent Application 07 00 1 076 . 4 in. The function and function of the hub transmission according to Fig. 1 can be illustrated with reference to Figs. 2 to j6, wherein the figures show the assistance for the different components of each rate stage and the specific power transmission path achieved thereby. The thick lines and arrows shown in Figs. 2 to 16 show the rotational power flow through the power transmission mechanism 4. The coupling of the various components and the power transmission path are shown in Tables 1 and 2 below, where Table 1 is for the coupling of the components and Table 2 is for the specific power transmission path. Table 1 Rate-stage clutch ring 55 (drive member and third planet carrier 33) First sun gear 11 Second sun gear 12 Third sun gear 13 Fourth sun gear 14 1 Free freedom Free freedom 2 Free lock free Free 3 Free Free Free Lock 4 Free Free _ Free Lock Free 5 Release Lock Free Free Lock 6 Release Lock Free Lock Free 7 Free Lock Free Lock 8 Free Lock Free Lock 9 Engage Lock Free Freedom 10 Engage Free Free Lock 11 Engage Free Free Lock Free 12 _ Engage Lock Free Free Lock 13 Engage Lock Free Lock Free 14 Engage Free Lock Free Lock 15 Engage Free Lock Lock Free-22- 200911619 Table 2 Speed Stage Power Transmission Path Gear Ratio 1 Drive Member - Fourth Clutch 54 - second ring gear 22 - (the fifth planetary gear 45 rotates around the fifth sun gear 15) - third planetary gear carrier 33 - third clutch 53 - first planetary gear carrier 31 - first clutch 51 - 0 hub shell. 426 2 drive member - fourth clutch 54 - second ring gear 22 - (the fifth planetary gear 45 rotates around the fifth sun gear 15) - third planetary gear carrier 33 - third clutch 53 - first planetary gear carrier 31-(the first planetary gear 41 rotates around the first sun gear 11) - the first ring gear 21 - the second clutch 52 - the hub shell 0. 545 3 drive member - fourth clutch 54 - second ring gear 22 - (fifth planetary gear 45 rotates around fifth sun gear 15) - third planetary carrier 33 - second planetary carrier 32 - (fourth The planetary gear 44 rotates around the fourth sun gear 14) - the first planetary gear carrier 31 - the first clutch 51 · the hub shell 0. 612 4 drive member - fourth clutch 54 - second ring gear 22 - (the fifth planetary gear 45 rotates around the fifth sun gear 15) - third planetary gear carrier 33 - second planetary gear carrier 32 - (third The planetary gear 43 rotates around the third sun gear 13) - the first planetary gear carrier 31 - the first clutch 51 - the hub shell 0. 694 5 drive member - fourth clutch 54 - second ring gear 22 - (fifth planetary gear 45 rotates around fifth sun gear 15) - third planetary carrier 33 - second planetary carrier 32 - (fourth The planetary gear 44 rotates around the fourth sun gear 14) - the first planetary gear carrier 31 - (the first planetary gear 41 rotates around the first sun gear 11) - the first ring gear 21 - the second clutch 52 - the hub shell 0 . 782 6 drive member - fourth clutch 54 - second ring gear 22 - (the fifth planetary gear 45 rotates around the fifth sun gear 15) - third planetary gear carrier 33 - second planetary gear carrier 32 - (third The planetary gear 43 rotates around the third sun gear 13) - the first planetary gear carrier 31 - (the first planetary gear 41 rotates around the first sun gear 11) - the first ring gear 21 - the second clutch 52 - the hub shell 0 . 887 7 drive member - fourth clutch 54 - second ring gear 22 - (the fifth planetary gear 45 rotates around the fifth sun gear 15) - third planetary gear carrier 33 - second planetary gear carrier 32 - (fourth The planetary gear 44 rotates around the fourth sun gear 14) - the first planetary gear carrier 31 - (the second planetary gear 42 rotates around the second sun gear 12) - the first ring gear 21 - the second clutch 52 - the hub shell 0 . 997 -23- 200911619 8 Drive member - Fourth clutch 54 - Second ring gear 22 - (5th planetary gear 45 rotates around the fifth sun gear 15) - Third planetary carrier 33 - Second planetary carrier 32 - (the third planetary gear 43 rotates around the third sun gear 13) - the first planetary gear carrier 31 - (the second planetary gear 42 rotates around the second sun gear 12) - the first ring gear 21 - the second clutch 52 - Hub shell 1. 130 9 drive member - fifth clutch 55 - third planetary gear carrier 33 - third clutch 53 - first planetary gear carrier 31 - (first planetary gear 41 rotates around first sun gear 11) - first ring Gear 21 - second clutch 52 - hub shell 1. 279 10 drive member - fifth clutch 55 - third planetary gear carrier 33 - second planetary gear carrier 32 - (fourth planetary gear 44 rotates around the fourth sun gear 14) - first planetary gear carrier 31 - a clutch 51 - hub shell 1. 437 11 drive member - fifth clutch 55 - third planetary gear carrier 33 - second planetary gear carrier 32 - (third planetary gear 43 rotates around the third sun gear 13) - first planetary gear carrier 31 - a clutch 51 - hub shell 1. 630 12 drive member - fifth clutch 55 - third planetary gear carrier 33 - second planetary gear carrier 32 - (fourth planetary gear 44 rotates around the fourth sun gear 14) - first star gear carrier 31 - (the first planetary gear 41 rotates around the first sun gear 11) - the first ring gear 21 - the second clutch 52 - the hub shell 1. 838 13 drive member - fifth clutch 55 - third planetary gear carrier 33 - second planetary gear carrier 32 - (third planetary gear 43 rotates around the third sun gear 13) - first planetary gear carrier 31 - ( The first planetary gear 41 rotates around the first sun gear 11) - the first ring gear 21 - the second clutch 52 - the hub shell 2. 085 14 drive member · fifth clutch 55 - third planetary gear carrier 33 - second planetary gear carrier 32 - (fourth planetary gear 44 rotates around the fourth sun gear 14) - first planetary gear carrier 31 - ( The second planetary gear 42 rotates around the second sun gear 12) - the first ring gear 21 - the second clutch 52 - the hub shell 2. 341 15 drive member - fifth clutch 55 - third planetary carrier 33 - second planetary carrier 32 - (third planetary gear 43 rotates around the third sun gear 13) - first planetary carrier 31 - ( The second planetary gear 42 rotates around the second sun gear 12) - the first ring gear 21 - the second clutch 52 - the hub shell 2. 656-24- 200911619 In summary, the hub transmission according to the described embodiment of the invention allows for a 15-speed internal hub transmission in which the diameter of the hub shell 2 is similar to that of the currently available 8-speed hub transmission diameter. This means that the hub transmission of the present invention provides more speed grades than conventional hub transmissions without increasing the hub diameter. In addition, the hub transmission according to Fig. 1 provides a simple and advantageous point of all transmission paths, which results in efficient power transmission. In general, the planetary carrier 3 1 of the downstream planetary gear mechanism 6 has an axially elongated shape engageable with the planetary gears 43 of the upstream planetary gear mechanism 8. Further, the axially elongated shape of the planetary carrier 3 1 allows the planetary gear carrier 31 to be coupled/separated from the planetary carrier 33 of the more upstream planetary gear mechanism 9. In particular, the axially elongated planet gear carrier 31 of the downstream planetary gear mechanism 6 selectively transmits rotational power from the planetary gears 43 of the upstream planetary gear mechanism 8, and is selectively movable from a more upstream planet. The planetary gear carrier 33 of the gear mechanism 9 transmits rotational power. The axially elongated shape of the downstream planetary carrier 3 i allows for a small 'small diameter internal hub transmission for bicycles having an extremely efficient transmission path. BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a longitudinal cross-sectional view of a hub transmission in accordance with an embodiment of the present invention. Figure 2 is a longitudinal cross-sectional view of the hub transmission in accordance with the Figure at a rate level. -25- 200911619 Figure 3 is a longitudinal section view of the hub transmission according to Figure 1 at a speed stage 2. Figure 4 is a longitudinal cross-sectional view of the hub transmission of Figure 1 at a rate level 3. Figure 5 is a longitudinal cross-sectional view of the hub transmission of Figure 1 at a rate level 4. Figure 6 is a longitudinal cross-sectional view of the hub transmission of Figure 1 at a rate level 5. Figure 7 is a longitudinal cross-sectional view of the hub transmission of Figure 1 at a rate level 6. Figure 8 is a longitudinal cross-sectional view of the hub transmission of Figure 1 at a rate level 7. Figure 9 is a longitudinal cross-sectional view of the hub transmission of Figure 1 at a rate level 8. Figure 1 is a longitudinal cross-sectional view of the hub transmission according to Figure 1 at a speed level 9. Figure 11 is a longitudinal cross-sectional view of the hub transmission of Figure 1 at a rate level i 。. Figure 12 is a longitudinal cross-sectional view of the hub transmission of Figure 1 at a rate level. Figure 13 is a longitudinal cross-sectional view of the hub transmission of Figure 1 at a rate level 丨2. Figure 14 is a longitudinal cross-sectional view of the hub transmission of Figure 1 at a rate level 丨3. -26- 200911619 Figure 15 is a longitudinal cross-sectional view of the hub transmission according to Figure 1 at a speed level 14. Figure 16 is a longitudinal cross-sectional view of the hub transmission of Figure 1 at a rate level 15. [Description of main component symbols] 1 : Turney shaft 2 : Drive member 2 a : Axial projection 2 b : Clutch engagement portion 3 : Hub shell 4 : Power transmission mechanism 5 : Shift mechanism 6 : First planetary gear Mechanism 7: Second planetary gear mechanism 8: Third planetary gear mechanism 9: Fourth planetary gear mechanism 1 0: Fifth planetary gear mechanism 1 1 : First sun gear 1 2 : Second sun gear 1 2 a : Axial Projection portion 1 3 : second sun gear 1 4 : fourth sun gear 1 5 : fifth center gear -27 - 200911619 2 1 : first ring gear 22 : second ring gear 22 a : axial projection 22 b : clutch engagement portion 3 1 : first planetary gear carrier 3 1 a : bracket portion 3 1 b : ring gear portion 3 1 c : clutch engagement portion 3 1 d : clutch engagement portion 3 1 e : Shoulder portion 3 2 : second planetary gear carrier 3 3 : third planetary gear carrier 3 3 a : clutch engagement portion 41 : first planetary gear 4 1 a : first planetary gear shaft 42 : second planetary gear 4 2 a : second planetary gear shaft 4 3 : third planetary gear 4 3 a : third planetary gear shaft 44 : fourth planetary gear 4 4 a : fourth planetary gear shaft 4 5: fifth planetary gear 4 5 a : fifth planetary gear shaft 5 1 : first clutch -28 - 200911619 52 : second clutch 53 : third clutch 54 : fourth clutch 55 : fifth clutch, clutch ring 5 5 a: lower or axial joint portion 5 5 b : upper or radial joint portion 6 1 : first sun gear guide ring 62 : second sun gear guide ring 63 : third center gear guide ring 64 : fourth center Gear guide ring 402: stepped planetary gear -29-